Transmission device



Feb.28,19.39. RQRBANL A l 2,148,857,

TRANSMISSION DEVICE Filed Jan. 24, 1954 2 sheets-shea: 1

'INVENTOR y '/P/c//A/P [en/v ATTORNEY Feb. 28, 1,7939.A R. vERBAN v ,2,148,857

l TRANSMISSION DEVICE Filed Jan. 24, 1954 2 sheets-sheet 2 ATTORNEY Patented Feb. 28, 1939 f Umreo ,is-#rares "TRANSMIS SION DEVICE Richard :E1-ban, Vienna ygAustria, ,assigner to yErban 4Patents Corporation, a corporation v of New vYork ApplicationlJanuary 24, 1934,Serial No.' 708,024

InAustria. Marchv 11; 1933 16; Claims.

My invention relates togears-an'dl-more' particularly tov friction gears, and' theobjectv-of my 'invention is to provide -forsuchv gears a' pressure device so designed-that by aslight axialrelative movement between two parts, axial pressures are produced, Whiclrarev proportionalx lto Athetorque ytransmitted Aby theA said` two lparts -and'v'whichare used to cause the parts ofrthe' gear which arefin frictionalengagement to bepressed against-each other. As a rule, such pressure devices comprise yopposed 4inclined-faces and twov or more rolling bo dies," er ,-g; vballs orl rollers; provided `between said faces. Wherethe angle of pitch ofthe vinclined faces is comparativelygreat, the rolling'bodies lare frequently omittedfin'which'event the nclined faces, which inthat'case usually have/the yshape 'of `helical `faces arein direct mutual sliding engagement. In alljcases,I the-torque is imparted to the" onepart' of the pressuredevice, which Y'may loe-secured to the gear vshafta and-is Vtransmitted by the other-part whichmay-be secured-toV a' gear Aelement' loosely vmounted on-saidshaft. Therefore, the `axial force produced byf 'the pressure device'is proportionall to `the torque-which '-is' ex- "ertedby the'gear elementconnected-with the `pressure device. Where this 'torque is `relatively "smallywhile the required axial force-is-relatively Igreat-theinclined iacesusually have Ivery'small angles of pitch;A resulting in Variousy well-known drawbacks. I"Moreover, )with such a pressure device, itis irripossible to 'produce axial forces the variations of which are'f'proportional to the'variations of the sum or thefdiierence of the torques `which are exerted by the various-parts of the gear.

The pressure device, according to the present invention, is so designed that the torque used for the lproduction of ythey axial'force is `imparted to thepressure device by an intermediate transmission. Bysuch a transmission, the producedl axial forces can be increased corresponding to Lthe ratio vof transmission. Furthermore; such" a transmission enables the pressure device to-be connectedvwith various partsiof Athe gear,1sothat the'torque effective in' the pressure device corresponds to the sum, or `the diierencemf a plurality of various torques',.whi1e, moreover, said-sum, or difference, or one of its .components can, be

Vincreased* or decreased,;dependng onthe ratio of transmission of the transmittingsystems.used. The ratio oftransmission can. also .be variable,

korfcan bey controlled fromthe outsideso .that .the

produced axial yforce Arcan. .bev made .Y dependent, to

any,.desiredextent,y on .the torque` las wellfas .on

-ot-herfactors;suchasnthe ratio oftransmission of the gear',` the Velocity of theparts etc.

In the accompanying drawings, in `which I have shown, by v Way of"il1ustration,.various embodiment's'of my? invention,--"Fig. 1 lista perspectivediagrammatic view of a simple` embodiment of the invention, -whileSlFigi-Z risallongitudinal sectional AView ofpthisr embodiment;l Figs..3 and'4 are views similar to Fig. 1A showinglmodications;

ther l embodiment '-Fig.y 6 -is Aawdiagrammatic lillustration !of=the ratio kof transmission ofzthetembodiment shown byFig; 5;Figs. Pland 8.arediagramsV showing the various axial"forces produced.

liig.l lfillustrates-how by.I means of a system 0I levers theraxial /forcef producedby-the pressure device-is increased byl an increase of thetorque impartedto the'pressure device.

l indicatesl theV commongearshaft,1on..which is rotatably and axially movablymounted agear element, indicated-by 2, and adapted to rotate in the direction-of the arrow-'3. ii Thegear.Y element 2 is'connected-rwithy the` shaft lv by. means-of a This :pressure deviceiis represented l I whichis articulately connectedwith: the parts '2; il andi, as indicated at` l2,."l3 and d4 respectively.

-If the distance Ybetween Zand 5 is Ldesignated as a andkthe distancew-betWeen-A: and-".5.1as-b, the vperipheral force 16. acting on thefpair of. inclined .faces 8. at the-.ratio aib-is greater y'than :theI force `which would be.: activeat those' inclined'` faces,

if :the parts 2 and 4were.rigidly connected'with each other. vvIn^the lsameproportion, also, kthe axial force l1 producedA bythelpressuredevice 8,

8 and all) iszincreased. Thereforegthere is veffectiveinthe pressure'device a greater torque `than vthe torque T2 originally transmitted by. thepart 2, `said greater torque being ,The part 5, in turn, transmitsto shaft l only, a .torqueTZ in the direction of'thearrow'lgthat is, i

Fig-'521s a zlorrgtudinalrsectional viewof. arfurk10 in the same direction as the part 2 as shown by the arrow 3. It is obvious that by a corresponding selection of the ratio of transmission azb, any desired torque can be made to act in the pressure device 8, 9 and l0 and that thus the angles of pitch of the inclined faces can be made of any desired size. With small angles of pitch, the use of intermediate rolling bodies IU is indispensable because with a. gliding friction the resistance against movement would be too great to permit safe operation of the device. In case 'of an angle of pitch which would be smaller than the angle of friction, the device would not operate at all. On the other hand, with an angle of pitch of about 45 or 60, the effect of the angle of friction of the gliding friction is Very small (scarcely 10% depending on the character of the two gliding surfaces), and under these circum-l stances, it is possible to dispense with intermediate rolling bodies in the construction of pressure devices and thus to produce pressure devices which act proportionately to the variations of the transmitted torques.

The embodiment shown by Fig. 2 in longitudinal section corresponds to the diagram illustrated by Fig. 1. At 2l is shown the gear shaft, on which is secured the part 22, which is provided with a plurality of V-shaped inclined faces 25 distributed over its circumference. At its outer end, the part 22 has a plurality of cavities 28, one of which only is shown in Fig. 2 in section. The parts 23 and 24 are rotatably mounted on shaft 2|; the part 24 represents a race-ring of a friction gear, the torque of which shall be transmitted to shaft 2|.by the pressure device. The part 23 is provided with V-shaped inclined faces 26. Between these and the opposed inclined faces 25 of part 22 are provided balls 21, one of which only is shown. The part 23 is provided at the outer end with a kplurality of radial slots 32 so distributed along the circumference as to be located directly opposite the cavities 28 provided in part 22, as well as opposite similar cavities 34 provided in part 24, as shown in Fig. 2. The transmission between the parts 22, 213 and 24 comprises rods 29, which at their ends are provided with ball-shaped heads 39 and 3| respectively, which respectively fit the cavities 28 and 34. The rods 29 also are provided intermediate the heads 30 and 3l with a ball-shaped enlargement 29 fitting the radial slots 32 of the part 23.

From the foregoing, it is obvious that upon the rotation of part 24 all the rods 29 are also moved about shaft 2l, which results in an increased torque being produced between the parts 22 and 23. On the assumption that the cavities 28 and 34 are spaced alike from shaft 2|, the effective transmission is equal to the ratio of the distances 30-3l to 30--29. When the device is in operation, the parts 23 and 24 also turn relatively to each other, so that for the transmission of the axial pressure produced by the pressure device 25, 26 and 21 from the part 23 to part 24 there must be interposed between said two parts a ball bearing shown at 35, in order to reduce the friction. However, since the relative Inovements between 23 and 24 are very small, the balls 35 can also be replaced by radially disposed lcylindrical rollers moving on the parallelly provided between the parts 22 and 23, without the operation of the device being in any material way changed thereby.

In the diagrammatic Figure 3, a construction is illustrated, in which two different torques of the same direction act, partly direct and partly increased by a transmission, on a pressure device. At 36 is indicated the shaft, to which is secured the part 39 provided with the inclined faces 46. Opposite the latter are disposed the inclined faces 42, which are provided on a part 4l, which is rotatably and axially movably mounted on shaft 35 and which at its upper end carries a lateral projection 41, parallel to shaft 35, constituting a fulcrum for a lever 46. At 44 and 45 are shown other parts rotatably and axially movably mounted on shaft 35. On the part 44 there acts a torque T44 in the direction of the arrow 31, while on the part 45 there acts a torque T45, in the direction of the arrow 38. Therefore, also, the part 39 secured to shaft 36 will rotate in the direction of arrow 38. Between the inclined faces 40and 42 is provided a ball 43. The part 44, by a joint 53, is pivotally connected with the free end of a lever 45, while the other end of this lever is pivotally connected by Ya joint 55 with the part 45. At 49 there is pivoted to the part 4l another lever 48, which by a joint 5l is connected with the part 39, and by a joint 50 with the part 45. Y

The operation of this construction is as follows:

If it is assumed that the two torques T44 and T45 are of such a size that the force 54 produced at the joint 53 balances the force 51 produced at the joint 58 in respect of the fulcrum 52 of the lever 45, the sum of the two torques is supplied to the part`4l by the lateral projection 41 and then, by means of the pressure device 42, 4,3 and 48 to the part 39 and thus to the shaft 36. Now, if, for example, the torque T45 is greater in relation to the torque T44 than is required for the state of balance hereinabove assumed, the balance between the reaction force 55 and the torque 51 produced by the torque T45 is disturbed at the joint 50, and since the force 51 is now greater than the force 55, the excess of force will operate the lever 48. Thereby, the pressure device 42, 43 and 45 is moved in the same direction as by the sum of the torques supplied through 52, 41 and 4|. The total axial force thus produced is, therefore, larger than corresponding to the sum of the two torques T44 and T45.

Now, if, on the other hand, T45 is smaller than corresponding to the state of balance of the lever 46, the force 56 at the joint predominates, and the `lever 46 is moved in the direction of the force 55 with the excess of force between 56 and 51. As a result of this movement, the pressure device 40, 43 and 42, by the lever 48, is partly relieved from `the effect of the total force 55 acting at the joint 52. Therefore, an axial force is produced which is smaller than would correspond to the sum of the torques T44 and T45. Thus, a construction is provided which at any desired selective definite ratio between T44 and T45 produces -an axial force proportional to the sum of these two torques. If this ratio is changed in favor of T45, the produced axial force is greater than the sum of the torques, and it is the greater, the further the ratio is changed in favor of T45. If the ratio between T44 and T45 is changed in the other direction, that is toward T31, the produced axial force of the pressure device is smaller than corresponds to the sum of the above said torques. In this manner, the produced axial forces for agrkiso' 'almost-ail types `of 'gears *with avariable trans- In Fig. f4 .1I Ilieve diagrammatioaily illustrated antl'ier fc'nstructionfin which one "of the two torquesfis -`4supplied direct to the 'pressure device, while 'the fsecfond "torque 'isffirnparted 'to' the pre'ssui'e device afte'rfa variation of f it'ssize, `andafter its "direction of rotationihasbeen reversed.

'At T4 lis v'indicated theishafh to'which issecured the part '59 carries the 'inclined `rfaces 6|). Opposed to them'f-areithe inclined faces 63 which are provided on a part shown avez; part 6-2 is "rotatably-and axially 'movably mounted on shaft 14. ABetween 'the inclined faces" 60 an`d"63 iS 'di's` posedthe ba1l`'65. On'e''f `the Ztwo torques T52 issuppliedfdirec'tA to thepartv 62, whichthereby'is rotated in'thedirectioii'of the arrow 68. At |56 is "'hown f-zar-part which, "like part Y'62, is r'otatably and l-aaxially iovably mounted on `shaft 14; part 66 is 'subjected '-to'a `torque T66, which tends t0 rotate \the' part the direction of thefarrow V61, that `is,f%in fa direction opposite "to part 62. l'The y torque rT66 is' designed A'toact 'on y"the pressure device"6"0, *63 and '65 in"the 'same direction as T62, and in an increased degree. To lthis e'nd, thereds .pivoted to thefpart -5`9f'at '10 a lever 1|, whichbyiajoint11'3isvalso' connected with part 62 'rid lby '='a' fjint "l2 with the Vlllrt 66. 'The forces' actingiat'the joir`1ts"12and 13'are 'indicated as regardsitheir direction 'by'small arrows. rIt is obviousthat'bec'ause of the ratio of transmission of thelever 1L-*there is exetedonthe part 62 a for-'ce @of "an f'incre'ased torque in the direction of the larrow 168. -The torque transmitted by the parti59t`ofsh'aft T4 is in the direction vrf the arrow 89,a's long-fas 'T62 `is "greater than TSR-andas regards its size "corresponds to the differencev between `fsaid two torques.l 'If the torques vare "of equal sizeandif the ratio of the arms of the lever l 1| y'is 1: 1, f the torque transmitted 'to v'shaft -14 is nil; "and stilLthere is produced by the pressure device`68j65 and 63'an axial/force corresponding to' 'a torquel ofthe ksize 411g-(T62 trat) ivFig. j 5 "shows "an embodiment of the Vdiagram Iillustrated'in Figi. A'Ihe gear shownfinFig. 5 y C tn gear'"prt'dt-Jdy "With adjustable 'fricollespermitting the' variation of' the transonjifatio iripfrtoV 11:1;the drive shaft andthe n 'shaftirritating''l in the same direction. Y y l1 5 is shownthe'driveshaft to 'which is secured'fthe rollersupport 11, on which arerotatfablv mounted aI plurality of (non-adjustable) r1lers`i18. Thesefr'nove, onthe one hand, on therace-ring 19,ff'reely rotatable on Vshaft 15, and,`ontlie-otherhand, onv a track of the'r'aceringll, jrotatably mounted yon the' driven shaft 16, f'To the' latter is secured the roller support 83 'of theadju'stable or' tiltablevrollers 82, and the shaft `-16 rotated by the'rotationv of said suprt' 831 Theradjustmentof'the rollers 82, for the :purpose of 'varying' the 'ratio 'of transmission, can be effectedfby-ai'jmeans 'of fwell-known constructin,-as`indicated in Fig. 5 Vby'a sleeve 84 ir ded with'f'a grooved collary 85. The rollers slightly axially movable iso Athat-by the 1nut 81 :it can be adjusted withlnfnarrow limits.

When the race-ring 19 'is iheld against rotation and the 'drive-'shaft *15 is rotated, the race-'ring 8D is rctatedbythe rfriction `rollers 18'at greater speed :than `the shaft 15.

Now, if also 'the'r'ace-ring f8| yis held l'against rotation, the froller-support and thereby also the driven shaft 16 are rotated, because the adjustable Vrollers 82 Ymove .like planetary gears. Depending'on the positionof1the'rollers`82, the number `of revolutions '-of 'the 'roller ksupport 83 and of the 'shaft 16 varies. In `the positionof the rollers -82 vsh'own i'n Fig. 5, the number of revolutions `is `Igreatest, 'andsubstantially like the number vof `revolutions of the driving shaft 15. If the irollers 82 yare Ymoved from the position shown clockwise, thenumber 'of revolutions of shaft 16 becomes smaller. The moment of reaction of the gear occurs `at two parts of the gear, that yis to say, at=the race-ringl and the race-ring 19. The moment of reaction of the race-"ring 19 'acts :in v*the fsame direction as `the driving moment; while the moment 'of reaction of the race-"ringf8l is oppositeto that'direction. Now, if the gear 'runs Awith -a ratio of 'transmission of 1:1, vthe `two 'moments 'of reaction are equally largeyas will 'appearlfromFig 5, if'one considers that in that case the torques at the drive shaft i15 and atthe fdriven shaft 116 are equal to each other. However, since, as hasfalready been stated, the moments of reaction 'of the rings-8| 4and`19 haveopposite direction, that is to say, tendto rotate said-rings in'opposite direction, the -two ymoments of reaction balance eachother, and ftheitotal "moment of reaction of the-gear is nil. yFor-the otheripositions'of *the adjustable roilers-82 the` moment ofreaction-of the racering-8| -pre'dominates, sothat there remains a positive total momentof reaction-the term positive being' usedvfor a-reactionmomerit which :has the opposite ydirection vof :the driving torque. Now, if`theaxialforce of pressure between'the rollers 82-and' the race-rings 80,-8I in every position of the rollers-82fhas a value; which as nearly as possible, approaches the required valueftheaxial lforce exerted onthe gear must be proportional to the torque of shaft'16. control of the axialforce'proportional to the'torque of one of the two rings `-would result in'consid- 'erably Apoorer y'conditions and'a *great excess of load, as has-been-fully explained inmy cependying application, 'Serial No. 679,843, vfiled on July 11, l1933. However, vthe sum of the "torques o'f the race-ringsf80,f8 Iv can ybe used for adjustment, since said-summust always be equal to the torque of 'the roller carrier 83.

In the embodiment shown, the"torque of `the race-ring -8| isy transmitted in a -simple 'manner by means of apress-ure device 'now-to be described. Atf'the right hand endof theI cylindrical casing-'8B there is -secureda collar '88,' "which is provided with 4inclined faces 89. Another co'llar 99 provided with :similar inclined f faces '9| bears, by means -of-bal1s-93, 'against-the-race-ring 19, and is so disposed'that space is providedfor the yballs 92 between the inclined faces5 89',` 9|. Now; if the collar'98 is'prevented from rotation, but is allowed to move axially, there will bezproduced in the pressure v'device 89, 92,"va'ndt9l fan-'raxial force, which is proportional'to ther torque of the'race'- ring 8|. yThe col1ar`9|l canbeheld againstY rotation; for "example," by' ahollow Shaft' '94 ,'f'which" on its periphery "carries 4fa fbrakeldrum 95. By Pa brakebandgr, say,ra1zne11oa1frlat spring 96,the

said drum 95 can be prevented from rotation. The arrangement may besuch, that'the drum is prevented from rotation in one direction only, but is free to rotate in the other direction. 'Ihe above described pressureY device corresponds to the parts 59-52 in Fig. 4, the collar 90 corresponding to thepart 59, the hollow shaft 94 to the shaft 14 and the collar 88 to the part 62 of Fig. 4.

It has been shown supra that the correct axial force wouldV be produced, if there were transmitted by means of a pressure device a torque, corresponding to the algebraic sum of the torques of the two race-rings and 8|. Now, the moment of reaction of the ring 19 is at a constant ratio to the torque of the ring 80. It is decreased only 'in proportion to the sliding radius of the rollers 18 on the two rings 80 and 19 and moreover, as has been stated above, has the opposite direction of the torque of race-ring 8|. Therefore, the torque of the ring 19 would have to be decreased in proportion to the transmission effected by the rollers 18, and reversed so that together with the torque of the ring 8| it would result in the required total output. To this end, there is provided in Fig. 5, in place of a simple lever transmission, a transmission by means of teeth, as illustrated in Fig. 6 by the partial circles and the eiective lever arms. The ring 19 is provided on its circumference with teeth indicated at 91, which teeth are in mesh with teeth 98 of a sector 99 rotatably mounted on a pivot |00 secured in a projection |0| ofthe casing 86. Said sector 99 has a second rim of teeth |02 in mesh with a set of teeth |83 provided on `the brake-drum 95. This construction corresponds to the lever 1| in Fig. 4, with the sole exception that said lever can be axially displaced, while the transmission shown in Fig. 5 acts radially. To the fulcrum 10 of lever 1| (Fig. 4) corresponds the point of contact |05 of the partial circles |02 and |03, which for the sake of simplicity are designated by the same reference numerals in Fig. 6 as the rims of the teeth in Fig. 5. To the joint 12 in Fig. 4 corresponds the point of contact |04 of the partial circles 91 and 98 and to the joint 13 the axis of rotation |00 of the toothed sector 99. In the calculation of the eifective leverage the fact,.of course, must be taken into consideration that the points |04, |05 and |00 lie in different radii.

If the drive shaft 15 rotates in the direction of the arrow H0 (Fig. 6), the ring 19 provided with the rim of teeth 91 will also rotate in the same direction, that is, in the direction of the arrow |06. The ring 80 also rotates in the direction of the arrow |06, while the ring 8| v tends to rotate in the opposite direction, that is, in the direction of the arrow |09 (Fig. 6). The peripheral force |01 in the partial circle 91 is transmitted as force |08 on the axis |00. There occurs at the point |05, that is, in the partial circle |03 of the brake-Y drum a force of reaction I. To the force |08 corresponds a torque transmitted to the casing 86 of the same size as the torque of the ring 80. The total torque composed of the torques of the rings 80 and 8| in the casing 86 is transmitted by the pressure device 89, 92 and 9| to the brakedrum 95. To this total torque there corresponds in the partial circle |03 a peripheral force ||2. When the gear transmission is 1:1, the forces and ||2 are equal and, therefore, balance each other; (The losses by friction are ignored.) In that case, the total moment of reaction of the gear is nil, and yet the construction above described permits by means of a single pressure device actuated `by the moments of reaction to produce the axial force, proportional to the torque transmitted from shaft 15- to shaft 16, for exerting pressure on the gear.

The gear construction above described can also be used with slight changes in respect to the drive shaft and the driven shaft as a so-called differential gear, in which event, with the same arrangement of the pressure device, the axial force required in each case is likewise produced.A It is then only necessary that the shaft 15, or the roller carrier 11 connected therewith, remain at rest, while the hollow shaft 94, or the brake-drum 95, must be driven. The driven shaft 16 remains connected with the roller carrier 83. In this case, one obtains a range of number of revolutions of the drivenshaft 19 from about 0.7 of the number of revolutions of the driving shaft 15 to stop, which occurs inl the position of the rollers shown in Fig. 5. When the angle of inclination of the rollers 18 is smaller than the greatest possible angle of inclination of the rollers 82, one obtains numbers of revolution of the driven shaft 10 beyond the zero point in the reverse direction.

In the case of the described gear construction,

it is especially important that the produced axial force is proportional to the torque of the roller carrier 83, because otherwise the gear would have to have much larger dimensions, to prevent it from being too quickly destroyed. This will be made clear with the aid of the diagrams of Figs. 7 and 8, in which the axial forces are shown on the axisof the ordinates and the various transmissions of the gear from 1:1 to 1:3 on the axis of the abscissae. Fig. 7 illustrates the axial forces which are produced by a pressure device, which is connected only with one of the rings 80 or 8|. The curve A0 shows the axial force required in order t-o insure at a constant torque at the driving shaft a transmission free from sliding. As will be seen, this axial force ascends rather in a straight line in-proportion to the transmission. Now, if thereV were connected a pressure device with the ring80, or with the ring 19, there would result the straight line Al, that is to say, the axial force is constant and has always the highest value which is about three times that of its lowest value. In other words, the pressures in the gear are as great as if the threefold amount ofv work were transmitted. The losses are correspondingly great and the life of the gear is short. On the other hand, if the pressure device were connected with-ring 8| only, the curve A2 would result. In that case, the overload at the high speeds would be avoided, but the axial force would rise considerably toward the ratio 1:3 and would be three times as great as would be required. For this reason, therefore, the gear would have to have much greater dimensions to prevent risk of destruction, or the gear would have to be operated with a fraction only of the normal load at all ratios deviating from the ratio 1:1. The overloads resulting in the cases just mentioned at various ratios are indicated by the hatched surfaces.

Fig. 8 illustrates the conditions for the construction shown in Fig. 5. The axial force produced by the united torques of the rings 19 and 8| is A3, while the axial force exactly requiredy for the power transmission is A0. It will be seen that the resulting overloads are very small. They can be still further reduced if by a suitable selection of the leverage difference between A0 and A3 Vnear the ratio 1:1 is still further reduced, and if then, according to the arrange- 2, 14a-sm:

ment: shown inlig. 3; from:the2point'whereA32 equals A a reduntiomv of thel axial force ieper mitted to take place toward the ratio 1:3. Suoni an:v arrangement becomes;` of course; a little more complicated than the one described' withf' refer@ ence toFig. whicninimostpractical instances will .f bei found" suflicient.

' What I claim.. and'- desi-retoasecure` by Letter-s1 Patent is:

1'. In a device of; ther classrdescribed, a mu-ltiA stage friction gearfhaving axed-ratiotrollingf body and? a race therefor` andi` a variable-ratiorolling' body-andiarace therefor, a pressure-de-A Lili.'

vice comprising two rotatable member-s, one offsaid pressure: members beingi rig-idly connectedf to the variable-ratio race; and gearsl between thels'aidi fixed-ratio raceandf the other-of sai-dpressurei members; toreverse the direction` off rotation-ofl thel saidfpressure-member and tovarythe torque appliedthereto;

21 A. device, according` toY claimt lf, whereinV the reaction of the saidf fixed-ratio race is intheopposite direction to that of the` said'- variablerati-o4 raceL so that, at a- 1f:1=` ratiol ofthe-latter; the said opposed reactions balance-each other; andl wherein the axiali-pressureproduced byv the said pressure: 'device will-be -proportionall to the torque transmitted and`x will be produced irrespective ofv` the absence ofA resultantY reaction'.

3; A deviceaccording-to` claim 12, wherein one` of the said pressure mem-bers is provided with a brakemeanstoA enable the-device to function differentially.

4. In a device of" theclassdescribed; amultistage friction gear'having roll-ing bodies-- in4 ad'- hesive driving contact with races, meansv4 for`-0pposing the torquereactions of the stages of said friction gear, said friction gear being arranged so that at a 1:1 ratio of transmission said reactions balance each other, and means including a pressure device operable at all times and even in the absence of reaction, to produce axial thrust in proportion to the torque being transmitted.

5. In a device of the class described, a multistage friction gear having races and rolling bodies therebetween and in adhesive driving contact therewith, said races being subjected to reactions of different magnitude, and means including a pressure device to produce axial pressure to maintain said adhesive driving Contact which is proportional to the torque being transmitted and which is independent of the magnitude of the reactions' on the said races'.

6. In combination with a power transmission system in which power is transmitted from a driving to a driven element by the adhesive driving contact of races with rollers therebetween, a torque loading device for generating a pressure for maintaining the adhesive driving contact of the rollers with the races, said device including two relatively movable elements, means for causing a driving torque impressed on the system to generate a plurality of torques in parallel relation to each other, and means for modifying said generated torques and applying them to said elements so as to generate pressure tok maintain said adhesive driving contact.

7. In combination with a power transmission system in which power is transmitted from a driving to a driven element by the adhesive driving contact of races with rollers therebetween, a pressure device for generating pressure for maintaining the adhesive driving contact between said rollers and said races, said device including two relatively: movabl'ef elements, torque modifying means operatively associated withsaid elements, andifmeansffor applying tosai'dtorque modif-ying; means a plurality:y oftorquesgenerated insaid system: and havinga parallel relation toY each other.

8f Incombi-nati'on withI af power transmission systemxinwhichpower istransmittedfromv a drivingy tov a driven element byv the adhesive driving contact of" races` with rollers therebetween, a torqueloadingl device for generatingl pressure formaint'ainingthe adhesive driving'contact between said rollers andl said-races, said' device including twolrelatively movable elements, torque modifying lever means operatively connected to one of saidlelements at one point ofsaidlmeans and havingipivotalfconnect-ion` with the other of said elements at a-secondpoint thereof, means for applyi-ngJ a torque, generated in said system externally of'said torque-modifying means, to one of' said` elements, and means for applying another torque; generated in said' systemv externally of said lever means, to a third point of said torquemodifying means.

9; In combination wit-h a power transmission system in whichv power is transmitted from a driving to'a driven elementy by the adhesive driving contact of races with rollers positioned therebetween, a torque loading device forgenerating pressure for maintaining the adhesive driving contact between said rollers and said races; said device including tworelatively'movable elements; leverv means pivotally connected tov one of said' elementsat one point of said lever means and having pivotal connection with the other of saidelements yat a second point thereof, means for applying-a torque, generated in' said system` externally of said lever means, to one of said elements, and means for applying another torque, generated in said system externally of said lever means, to a third point of said lever means.

l0. In combination with a power transmission system in which power is transmitted from a driving to a driven element by the adhesive driving contact of races with rollers therebetween, a torque loading device for generating a pressure for maintaining the adhesive driving contact of the rollers with the races, said device including two relatively movable elements, means for causing a driving torque impressed on the system to generate torques in parallel relation to each other, means for applying one of said generated torques to one of said elements, lever means pivotally connected to said last-named element at one point of said lever means and having pivotal connection with the other of said elements at a second point thereof, and means for applying another of said generated torques to a third point of said lever means.

11. In combination with a power transmission system in which power is transmitted from a driving to a driven element by the adhesive driving contact of races with rollers therebetween, a torque loading device for generating pressure for maintaining the adhesive driving contact between said rollers and said races, said device including two relatively movable elements, torque modifying means acting as a lever operatively engaging one of said elements at one point of said lever and having pivotal connection with the other of said elements at a second point thereof, means for applying a torque to each of said elements, and means for applying another torque to said torque-modifying means at a third point of said lever. l

12. In combination with a power transmission system in which power is transmitted from a driving to a driven element by the adhesive driving contact of races with rollers positioned therebetween, a torque'loading device for generating pressure for maintaining the adhesive' driving contact between said rollers and said races,v said device including two relativelyvmovable elements, a member acting as a lever pivotally connected to one of said elements, at one point of said lever and having pivotal connection with the other of said elements at a second point thereof, means for applying a torque to one of said elements, and means for applying another torque to said member at a third point of said lever.

13. An infinitely variable system comprising races and rollers in adhesive contact therewith, a torque loading device comprising two .members and torque transmitting connections between each of said members and the said system, said members being angularly movable relatively to each other for causing an axial pressure between the races and rollers of the system, a third member movable relatively to the above said two members and means forming operative connections between the said third member and the said two members for modifying th-e said pressure in response to the said third member.

14. An infinitely variable transmission system comprising races and rollers in adhesive contact therewith, a torque loading device comprising two torque transmitting members angularly movable relatively to each other for generating an adhesive pressure between the races and rollers, a plurality of elements and each thereof being in torque transmitting engagement with each of the said two members, and a third torque transmitting member movable relatively to the said two members and pivotally engaging all of said ele ments.

15. An infinitely variable transmission system comprising races and rollers in adhesive contact therewith, a torque-loading device comprising two torque transmitting members angularlyV movable relatively to each other and adapted to spread apart and generate axial pressure incidental to such relatively angular movement, leverage means pivotally engaging, at spaced points thereof, each of the said two members, a third torque transmitting member movable independently of the said two torque transmitting members, and means causing a pivotal engagement between said third member and each of the saidv leverage means.

16. In a variable friction transmission comprising races and rollers, said transmission having a device for generating a pressure dependent upon the load imposed upon said transmission; means rendering said device eiective; Vmeans transmitting the pressure generatedrin said device to said races to maintain the driving contact between said rollers and races, and a mechanism for modifying the pressure generated in said device at a given load of said transmission, said mechanism comprising a member relatively movable with respect to said first named means which render said device eiiective and free to move axially with respect to said second namedmeans for transmitting the pressure generated in said device, and operative connections between said member and said device whereby the pressure generated varies in accordance to ther combined influence of the load upon the transmission and the relative movement of saidmember. Y

RICHARD ERBAN. 

